Clutch and brake mechanism



June 11, 1946.

E. K. -[QHANSEN CLUTCH AND BRAKE MECHANISM Filed May 24, 1943 3 Sheets-Sheet 1 June 11, 1946.

E. K. JOHANSEN 2,402,052

CLUTCH AND BRAKE MECHANISM Filed May 24, 1943 3 Sheets-Sheet 2 June 11, 1946. E JOHANSEN' V 2,402,052

CLUTCH AND BRAKE MECHANISM Filed May 24, 1943 3 Sheets-Sheet 3 30 77 r 35 35 34 p 56 r Q F 70 Q 3? Patented June 11, 1946 CLUTCH AND BRAKE MECHANISM Einar K. Johansen, Chicago, Ill., assignor to Clearing Machine Corporation, Chicago, Ill., a corporation of Illinois Application May'24, 1943, Serial No. 488,192

4 Claims. 1

This invention relates to improvements in clutch and brake mechanism, particularly adapted, though not necessarily limited in use, for large and heavy presses operating at high speed.

Heretofore, with presses of this character, it

has been customary to arrange or mount the controlling clutch upon the power driving shaft of the press, with the result that when starting the press, it is necessary to start to rotate, or actuate, all of the movable parts, which constitute a very heavy mass, and this requires considerable power, with a resultant strain upon the clutch mechamsm.

It is one of the objects of the present invention to overcome these objections and difficulties, and to provide an improved clutch mechanism which is mounted upon the crank shaft, that is, the shaft which directly imparts motion to the slides of the press, with the result that only the driving mechanism will be initially started in operation.

Subsequently thereto, and at the will of the operator, the clutch may be rendered active to transmit such motion to the crank shaft, thereby reducing materially not only strain upon the clutch, but also the volume or mass to be initially moved upon starting of the operation of the press.

Heretofore, with presses of this character, it has also been customary to provide the clutching and braking mechanism at opposite ends of the power shaft. In the present invention there is provided a clutch and brake mechanism connected with the crank shaft, both atthe same end of the shaft. Furthermore, with the present in-? vention there may be providedlboth a clutch and I hereinafter more fully described and claimed, and shown in the accompanying drawings illustrating this invention, in which:

Fig. 1 is a front elevation of a portion of a press having clutch and brake mechanism applied thereto, constructed in accordance with the principles of this invention.

Fig. 2 is a side elevation of Fig. 1.

Fig. 3 is a vertical sectional View of one end of a crank shaft and a part of a press frame, showing clutch and brake mechanism and the means for releasing the brake, constructed in accordance with the principles of this invention, applied to the crank shaft. t Fig. 4 is a right-hand elevation of Fig. 3, with parts omitted.

Fig. 5 is an enlarged detail sectional view of a portion of the clutch and brake mechanism at one end of the crank shaft showing the spring means for rendering the clutch mechanism inactive.

Fig. 6 is a detail sectional view taken through the spring means for rendering the brake mechanism active and the clutch mechanism inactive.

Throughout this specification and claims, the shaft to which the clutch is connected, or upon which it is mounted, will be designated as a crank shaft, but it is to be understood that such term is not to be considered as a term of limitation, but is to be construed broadly to include either a shaft having a, crank portion or a shaft having an eccentric (as shown) connected therewith and provided with a co-operating eccentric strap, which latter forms the connection with the slide of the press.

Referring more specifically to the drawings, the numeral l0 designates a main operating shaft, which may be a crank or an eccentric shaft and is mounted in the frame ii I of the press, Carried by the shaft is one or more eccentrics l2, according to the nature of the press, that is, according to the number of slides which are to be operated by the rotation of the crank shaft. Co-operating with each of the eccentrics i2 is an eccentric strap l3 which has a pivotal connection it with the slide l5, so thatupon rotation of the shaft, the=slide will be given a reciprocatory movement.

The numeral l6 designates a driving shaft which carries gears ll that mesh with gears l8, one of the gears I8 being located on each side of the press and encased within a housing l9, each housing being supported by the frame, Motion is imparted to the gear [8 to rotate .the latter in any suitable manner, such as from a. motor 20 which may be connected by a belt H with a pulley 22, the latter being secured to a shaft 23. This shaft 23 is provided with a' gear 24 that meshes with a gear 25 that is also connected to the shaft it, for the purmise of transmitting a rotary motion to the gear it.

As before stated, one of these clutch and brake mechanisms may be arranged at each end of the crank shaft Ill. and therefore the description of onewill apply equally as well to both of them. The shaft it carries a sleeve member 26 which is secured thereto and for rotation therewith, in any suitable manner, such as by means of a gib or key 21. The gear i3 is rotatable upon the sleeve 25, and, if desired, suitable bearing material 23 may be provided between the hub 29 of the gear l8 and the sleeve 26. The gear is is provided with a chamber 30 disposed at its center, and the wall of the chamber is provided with any suitable number of ribs or teeth 3! projecting inwardly.

Arranged within the chamber 30 are annular friction creating members 32, any number of which may be provided, and these members-32 are provided with teeth or recesses 33, each interengaged with the teeth or ribs 3| on the wall of the chamber 30, so that the friction creating elements 32 may rotate with the gear l8, and are also adapted for lateral bodily movements in directions lengthwise of the axis of the gear. The sleeve 25 is also provided, about its periphery, with teeth or ribs 34, any number of which may be provided, and annular friction creating elements 35 are mounted upon the sleeve 26 and are themselves provided with teeth or ribs 36 engaging or intermeshing with the teeth or ribs 34 on the sleeve 26, so that these elements 35 will rotate with the sleeve 26 and are also adapted for lateral movement in directions lengthwise of the axis of the shaft ill.

The friction creating elements 32-35 are alternately arranged with respect to each other,

and friction creating material may be provided on the proximate faces of adjacent discs, so as to create the necessary friction to cause all of these elements to rotate together, and to' frictionally lock the gear 18 with respect to the shaft l0.

A chamber 30 (or a plurality of separate and communicating chambers) in the gear is is, or may be, provided with a removable closure 31, and is-of such a size that a piston 38 disposed therein is adapted for lateral movement. Fluid pressure, which is admitted into the chamber 30, in a manner hereinafter to be described, will act upon the piston 33 to move it laterally and to force the friction elements 35-32 into engagement with each other, so as to lock the gear i8 and the shaft ill for rotation together. When, however, the fluid pressure in the chamber 30 behind the piston 38 is reduced, then the discs or elements 35-32 will be free to rotate, one with respect to the other, so that the gear 68 will then be unlocked from the shaft it to permit the gear to rotate independently with respect to the shaft. The front wall I9 of the housing is is provided with an opening 33 through which the end of the shaft l0 projects, and secured to the wall is and also encompassing the shaft it is an annular member es, and this annular member is provided with a chamber 4! closed by a closure plate 32.

Mounted upon the shaft id is a sleeve or collar 43 which is secured to the shaft for rotation therewith, and may be held in position in any suitable manner, such as by means of a key and an annular member 44 secured in position and to the shaft it by means of suitable fastening devices 45. This member 43 is provided with annular teeth or ribs 46 which are extended to any desired extent in a direction lengthwise. of the axis of the member 43. A friction creating member 41 is slidable upon the annular member 43,

and is provided with teeth or recesses encom passing the inner peripher, thereof, which interengage or intermesh with the teeth 48, so that the member 4? may be given a sliding movement ber 43. This member 41 projects into the space between the member 40 of the chamber 4| and the closure plate 42, and friction creating material 43 may be provided on the proximate faces of the adjacent parts,

The member 40 is provided with a chamber 49 in which is arranged a piston 50, and this piston may be either an annular member to conform to the contour of the chamber 49, or may be in the form of a plurality of separate pistons. A plurality of studs or members 5| are secured or anchored to the member 40, as at 5|, and pass loosely through the plate 42, as shown more clearly in Fig. 6. Encompassing each of these studs is a coiled spring 53, one end of which engages the member 42, preferably being seated in a recess 54. The other end of the spring contacts an adjustable nut or collar 55 on the threaded extremity 52 of the respective stud 5!. The spring 53 tends normally to force the member 42 in a direction to create enough friction between the members 40 and 42 to lock the shaft ill normally against rotation.

Disposed intermediate the member 42 and the piston 50, and also between the respective studs or members 51, is a series of pins or members 50, that-are mounted to slide freely in openings or bearings 50 in the member 40. These pins or members may be connected to, or may be separate from, the piston 50, and arelof a length to engage the member 42. Any number of these pins or members 50, and of the studs 5!, may be employed, and may be arranged in any suitable manner with respect to each other. The pins or members 50 serve as a means for moving the member 42 in one direction against the stress of the springs 53, and they also serve as a means for forcing back the piston 50.

When fluid pressure is admitted into the chamber 49, in a manner to be presently described, the piston 5il'will be moved to the right in Figs. 5 and '6, and cause the pins 50 to move the brake member 42 against the stress of the springs 53, to release it, thereby rendering the brake inoperative. When the fluid pressure is exhausted through the chamber H, and the passage 10, the springs 53 will act upon the disc or member 42, and return it to its original position; that is, to render the brake active. The piston 50 will, at the same time, be forced back to its original position by the pins 50*, as the pins will then be moved or shifted by the brake member 42. The elements 40-41-42 being released with respect to each other, permits the shaft iii to rotate with the gear wheel i8, when the latter is locked to the shaft. When the brake formed by the elements 40-41-42 is active to lock the shaft in against rotation, the clutch mechanism embodying the elements 32-35-38 will be inactive, so as to unlock the gear as with respect to the shaft ill.

Fluid pressure for controlling these parts may be supplied from any suitable source and delivered into a supply pipe 55, which latter has communication with a casing 51 that is held stationary with respect to the shaft [0. Within the casing 57 is a tubular member 53 that is secured to the shaft iii in any suitable manner, preferably by means of suitable fastening devices 59 passing through a hub 60. This tubular member 58 is preferably rotatably supported by means of ball bearings 5|; and has an opening 52 for the admission of fluid pressure from the pipe 33.

A chamber 63 in'the tubular member 58 has communication with a passage 64 in the shaft l0, and this passage 66 has communication with a passage 65 in a member '66 supported for rotation with the shaft I6. This passage 65, in turn, has

communicationwith a passage 61 leading to the.

chamber 30 in the gear wheel l8 behind the piston 38. With this construction, and when the fluid pressure flows from the pipe 56 through the opening 62, thence through the passages 64-66-61,. it will enter the chamber 30 behind the piston 38 to move the latter laterally, to effeet a clamping action of the elements 3235.

A tubular bearing 68 passes through the easing 51 and has communication with the passages 69, by means of which the bearing for the gear and between the gear and the shaft l0 may be lubricated. Leading from the pipe 56 is a branch pipe 16 having communication with a, chamber II which has communication, by means of a passage 72, with the chamber 49" in which the piston or pistons is or are located. If desired, a diaphragm 13 may be provided, against which the pistons 50 rest. With this construction, when fluid pressure is admitted into the pipe 56, a portion of the fluid will flow through the branch pipe 10 into the chamber H, and thence through the passage 12, to act upon the diaphragm 13; or, if desired, separate diaphragms for the pistons 50 may be provided, to force the diaphragm 13 against the pistons 50 to overcome the stress of the springs 53, to release the brake formed by the elements 60 4'l 42. The operation of the clutch formed by the elements 3235 is in opposition to the brake formed by the elements 46-41-42; that is, when one is active, the other is rendered inactive.

The fluid pressure is supplied from any suitable source, and in order to control the same, a suitable valve mechanism M may be provided, one for each of the mechanisms at the different ends of the shaft ill. .This valve mechanism may be of any desired or suitable construction well known in this art, the specificconstruction and the operation of which form no part of the present invention. Suffice it to say, however, that each of the valves M is adapted to be actuated by means of a suitable electro-responsive device, in the form of solenoids or other suitable devices, which will be rendered active or inactive. by means of suitable push buttons suitably arranged in a position convenient for the operator, so that by operating the buttons the gear to may be locked or unlocked with respect to the shaft ll]. Obviously, suitable packing will be provided at all points necessary to prevent leakage.

If desired, there may be provided an annular flange 76 on the front wall li-l of the housing l9, which flange projects inwardly, as shownmore clearly in Fig. 3, and may beprovided with an upwardly projecting annular wall 16. A plate or member 79 may be secured to the gear i8 to overlap thewall i8 and thereby provide a seal to prevent the lubricating material from being dissipated by the rotation of the gear Hi.

It is thought that the operation of this mechanism will be clearly understood from the foregoing, but, briefly stated, it is as follows:

When the press is idle, the gear I8 will be unlocked with respect to the shaft H), as at that time fluid under pressure will not be acting upon the piston 38, and the friction creating elements 32-35 will be free to rotate, one with respect to the other. The springs 53 will, at that time, move the member 42 inwardly, to render the brake active, and thereby'lock the shaftv lil against rotation. I

To start the press, the motor is operated, which will transmit a rotary motion to the gear l8, but as the gear I8 is unlocked with respect to the shaft ID, the shaft will remain idle and against rotation, by reason of the fact that the brake is active and will hold the shaft against rotation. After the desired speed has been given to the gear l8, or after the gear I8 is rotated, fluid pressure is admitted into the pipe 56, and being first admitted through the branch pipe ill, the brake will be rendered inactive by moving the pistons 50 under fluid pressure against the stress of the springs 63. The fluid pressure in the pipe 56 will then shift the piston 38 in the chamber 30, to render the clutch active to lock the gear l6 with respect to the shaft Ill, Thereafter, the gear l8 will rotate the shaft Ill until the fluid pressure is released, at which time the brake will then become active to stop and lock the shaft l0 against rotation, and the gear [8 will become unlocked from the shaft I0, and will be free to rotate about the shaft In.

With this construction, the fluid pressure will not only be supplied directly to operate the brake and clutch mechanism, but they will be operated simultaneously. Further, the operation. of the clutch mechanism will not depend upon or be controlled by the operation of any of the parts of the brake mechanism. 7

It will be manifest that in starting the press, considerable power is conserved and less kinetic energy will be required to start the press, because the gear I6 will be started to rotate under the power applied, without rotating the shaft l0. It is not until after the gear and all of the driving mechanism have been started in their rotation thatv the shaft It! will be connected to the gear.

In the specification and claims, the clutch and brake mechanisms are described in connection with a gear l8, bf it is to be understood that the mechanisms are also applicable to a fly wheel. Therefore, when the term gear" is employed, especially in the claims, such term is to be con sidered broadly to include either a gear or a fly wheel.

7 While the preferred form' of the invention has been herein shown and described, it is to be understood that various changes may be made in the details of construction and in the combination and arrangement of the several parts, within the scope of the claims, without departing from the spirit of this invention.

What is claimed as new is:

1. In a press, clutch and brake mechanism embodying a. main shaft, 9. gear mounted upon the shaft for driving it, a clutch and a brake mechanism adjacent the gear, one part of the clutch being mounted upon said shaft and another part being mounted upon said gear, the entire clutch mechanism being located within the confines of the lateral faces of the gear, a stationary casing or hood enclosing said gear and the said clutch mechanism, a portion of said brake mechanism being secured to said casing, said clutch embodying clutch discs normally in disengaging relationship, said brake embodying disc elements, resilient means normally holding said brake elements in locking relationship, and fluid pressure means operable against the pressure of said resilient means, to cause the brake elements to move into inactive relationship, the braking action being responsive to the action of said resilient means.

2. In a press, clutch and brake mechanism embodying a main shaft, a gear mounted upon the shaft for driving it, a clutch and a brake mechanism adjacent the gear, one part of the clutch being mounted upon said shaft and another part being mounted upon said gear, the entire clutch mechanism being located within the confines of the lateral faces of the gear, a stationary casing or hood enclosing said gear and the said clutch mechanism. a portion of said brake mechanism being securedto said casing, said clutch embodying clutch discs normally in disengaging relationship, said brake embodying disc elements, resilient means normally holding said brake elements in looking relationship, and fluid pressure means operable against. the pressure of said resilient means, to cause the brake elements to move into inactive relationship, and to also render the clutch mechanism active, the said fluid pressure means embodying cylinder and piston elements rotatable with said shaft.

3. In a press, clutch and brake mechanism embodying a main shaft, a gear mounted upon the shaft for driving it, a clutch and a brake mechanism adjacent the gear, one part of the clutch being mounted upon said shaft and another part being mounted upon said gear, the entire clutch mechanism being located within the confines o! the lateral'faces of the gear, a stationary casing or hood enclosing said gear and the said clutch mechanism, a portion of said brake mechanism move into inactive relationship,

being secured to said casing, said clutch embodying clutch discs normally in disengaging relationship, said brake embodying disc elements, resilient means normally holding said brake elements in locking relationship, and fluid pressure means operable against the pressure of said resillentmeans, to cause the clutch elements to and to also render the clutch mechanism active, the said fluid pressure means embodying a plurality of separate piston elements for rendering the brakemecha nism inactive.

4. In a press, clutch and brake mechanism embodying a main shaft, a gear mounted upon the shaft for driving it, a clutch and brake mechanism adjacent the gear, one part of the clutch being mounted upon said shaft and another part being mounted upon said gear, the entire clutch mechanism being located within the confines of the lateral faces of the gear, a portion of said brake mechanism being secured to a fixed support, and embodying disc elements, resilient means normally acting upon one of the brake elements for holding it in active relationship with another brake element, fluid pressure 'means for rendering said brake mechanism inactive and said clutch mechanism active, the last recited means embodying a piston element, and a member onerable by said piston. element and engaging one of the brake elements for moving the latter against the stress of said resilient means.

EINAR K. JOHANSEN. 

